JP2000088129A - Solenoid control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a solenoid control valve and to improve durability by constituting a movable part provided with a plurality of pressure response means and displacing with the pressure of control fluid to be a pressure response object and a solenoid, and switch controlling a valve means with energizing force corresponding to effective pressure receiving area smaller than each of these pressure response means. SOLUTION: A solenoid control valve 5 controlling coolant to a variable displacement compressor in an air conditioner according to suction pressure to the compressor is provided with a bellows assembly 52 and a solenoid 53 responding to crank chamber pressure Pc as valve driving means. The bellows assembly 52 is provided with a pair of bellows 52a, 52b which are different in effective pressure receiving area and a spring 52c energizing a valve element 54a in a valve closing direction. The bellows 52a, 52b which are coaxially opposed and arranged via an annular sleeve 52a are fitted and fixed into/to the annular sleeve 52e at fixed tip parts, are mutually connected by a rod 52d at movable tip parts and are displaced according to a pressure difference of external atmospheric pressure and internal pressure of the bellows 52a, 52b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a solenoid control valve. More specifically, the present invention relates to a solenoid control valve provided with a pressure responsive means that responds to the pressure of a control fluid, and relates to a technology that expands a pressure range of a control fluid to be pressure-responsive and has a small size and durability.

[0002]

2. Description of the Related Art In a variable displacement compressor used in an air conditioner or the like (cooling device), for example, the axial displacement of a swash plate set at a predetermined angle by swinging with respect to a rotating shaft is converted into reciprocating motion of a piston. In a swash plate type compressor that converts and compresses refrigerant, when the angle of the swash plate is fixed at a fixed value, the cooling capacity changes according to a change in the input rotation speed.

Therefore, the cooling capacity is adjusted by changing the angle of the swash plate according to the rotation speed of the swash plate and the required cooling capacity, and changing the reciprocating stroke of the piston.

In adjusting the cooling capacity, for example,
Since the temperature of the blown-out cold air (which is also related to the amount of blown-out cold air and the temperature before cooling) passing through the evaporator having an endothermic effect due to the vaporization of the refrigerant has a correlation with the suction pressure Ps of the refrigerant of the compressor ( When the cool air temperature rises, the suction pressure Ps rises, and when the cool air temperature falls, the suction pressure Ps falls), and control is performed to set the swash plate at a predetermined angle by utilizing the change in the suction pressure Ps.

[0005] The pressure of the refrigerant output from the compressor used hereinafter is the discharge pressure Pd, and the pressure of the crank chamber of the compressor in which the swash plate is arranged to set the swash plate at a predetermined angle is the crank chamber. The pressure is set to Pc.

(Prior Art 1) FIG. 16 is an explanatory view of a sectional configuration of a solenoid control valve 600 for performing such control, and FIG. 17 is a schematic view thereof.

[0007] The solenoid control valve 600 includes a pressure-sensitive portion 602 and a solenoid portion 603 on both axial sides of a cylindrical valve body 601.

The pressure sensing portion 602 is provided with a bellows cap 605 that fits into the opening 601 a of the valve body 601 and accommodates the bellows assembly 604. The inside of the bellows cap 605 is a bellows chamber 606.

The bellows assembly 604 disposed in the bellows chamber 606 has both ends sealed to holding plates 604a and 604b and a sealing portion thereof, and the inside thereof is sealed to a vacuum or a constant pressure (P ₀ ). A bellows 604c as a pressure response member is urged in the extension direction by a spring 604d.

The holding plate 604a fits into a depression 605b provided in the end face 605a of the bellows cap 605, and the holding plate 604b contacts the seat surface 601b of the valve body 601 to function as a valve body for opening and closing the valve portion 607. I do.

The solenoid portion 603 is provided with a plunger 603c that is attracted to the center post 603b by a magnetic force generated by a coil 603a to which a control current is applied and generates an urging force.

[0012] A balance rod 608 is provided to apply the urging force of the plunger 603c to the holding plate 604b as a valve.

The ports for controlling the fluid include a port 609 that opens into the bellows chamber 606 and sets the atmospheric pressure applied to the bellows 604c to the crank chamber pressure Pc.
When the valve portion 607 is opened and the valve portion 607 is opened, the crank chamber pressure Pc is released to the suction pressure Ps side.

In the solenoid control valve 600, the biasing force of the bellows assembly 604 is used as the biasing force in the direction to close the valve portion 607, and the thrust (biasing force) of the solenoid portion 603 disposed opposite to the bellows assembly 604. ) Is the biasing force in the direction to open the valve portion 607.

Then, by changing the thrust of the solenoid 603, the urging force for opening the valve 607 is changed, and the opening / closing valve force of the valve 607 is adjusted in balance with the urging force of the bellows assembly 604.

By controlling the flow rate from the crank chamber pressure Pc to the suction pressure Ps, the crank chamber pressure Pc is regulated, and the cooling capacity is adjusted (pressure regulation of the discharge pressure Pd) by changing the angle of the swash plate of the compressor. As a result, the suction pressure Ps is controlled.

The following equation (1) shows a balance equation for pressure control by the solenoid control valve 600.

Here, f0: bellows internal spring biasing force S1: bellows pressure receiving area S2: valve section pressure receiving area P0: bellows internal pressure Ps: suction pressure Pc: crank chamber pressure Fs: solenoid thrust.

[0019]

F0−S1 (Pc−P0) + S2 (Pc−Ps) = Fs According to Equation 1, each port pressure, the urging force by the bellows pressure receiving area and the valve part pressure receiving area receiving those pressures, and the solenoid thrust Although Fs is balanced, the variable width of the suction pressure Ps depends on the biasing force of the bellows assembly 604,
It is almost determined by the thrust of the solenoid 603.

The control pressure characteristic shown in FIG.
This is an example in which the influence of the crank chamber pressure Pc is eliminated in the control of s. If the bellows pressure receiving area S1 and the valve section pressure receiving area S2 at this time are S1 = S2, Equation 1 becomes
Equation 2 is obtained.

[0021]

F0-S1 (Ps-P0) = Fs Here, assuming that the suction pressure Ps is Ps1, Equation 2 becomes Equation 3.

[0022]

F0-S1 (Ps1-P0) = Fs1 Here, if the suction pressure Ps is Ps2, the following equation is obtained.
Is given by Equation 4.

[0023]

F0−S1 (Ps2−P0) = Fs2 Therefore, the variable width Ps1−Ps2 of the suction pressure Ps is as shown in Expression 5.

[0024]

Ps1−Ps2 = (Fs2−Fs1) / S1 From equation (5), the variable width of the suction pressure Ps is determined by the thrust variable width of the solenoid (Fs2−Fs1) and the bellows pressure receiving area S1.
Will be determined by

Under such a balance system, in the case of a conventional CFC-based refrigerant (R134a), the variable width of the suction pressure Ps needs to be about 5 kgf / cm ² , and the bellows pressure receiving area S1 is about 0.5 cm ² . Therefore, the required thrust difference of the solenoid is about 2.5kgf.

However, when a refrigerant having a high condensing pressure such as carbon dioxide or hydrocarbon is used as the refrigerant, the variable width of the suction pressure Ps needs to be about 20 kgf / cm ² .

At this time, the variable width of the suction pressure Ps is set to 20 kgf / c by the current thrust difference of the solenoid (2.5 kgf).
If the m ^2, the bellows pressure receiving area S1 is 0.125c
m ² , which requires extremely miniaturization, which makes fabrication extremely difficult.

Conversely, if the bellows pressure receiving area S1 is 0.5 cm ² at the present time, the difference in thrust of the solenoid is 10 kg.
f It becomes necessary, which leads to an increase in the size of the solenoid and an increase in required power.

(Prior Art 2) FIG. 19 shows a solenoid control valve 6 for controlling a compressor in the same manner as in the above prior art.
FIG. 20 is an explanatory diagram of a cross-sectional configuration of 50, and FIG. 20 is a schematic diagram thereof.

Contrary to the prior art 1, the bellows assembly 65
The urging force of No. 1 is the urging force in the direction of opening the valve portion 652, and the thrust of the solenoid 653 disposed opposite the bellows assembly 651 is the urging force in the direction of closing the valve portion 652.

The opening / closing force of the valve 652 is adjusted by changing the thrust of the solenoid 653 to change the urging force for closing the valve 652.

An axially opposed load is applied to the valve 652a of the valve section 652 by a bellows output rod 655 and a balance rod 656. A thrust in the valve closing direction is applied to the balance rod 656 by the solenoid 653.

The bellows chamber 657 and the solenoid 65
Plunger chamber 65 accommodating the third plunger 658
9 is a passage 661 passing through the valve body 660 in the axial direction.
And an axial hole 658a of the plunger 658, and a suction pressure Ps is applied to the plunger chamber 659.

By controlling the flow rate from the discharge pressure Pd to the crank chamber pressure Pc by the solenoid control valve 650, the crank chamber pressure Pc is regulated, and the cooling capacity is adjusted by changing the angle of the swash plate of the compressor (discharge pressure Pd Is performed, and as a result, the suction pressure Ps is controlled.

The balance equation for pressure control by the solenoid control valve 650 is shown in the following equation (6).

However, f0: bellows internal spring biasing force S1: bellows pressure receiving area S2: bellows output rod 655 pressure receiving area S3: seal part pressure receiving area of valve portion 652 S4: balance rod 656 pressure receiving area P0: bellows internal pressure Ps: suction Pressure Pc: crank chamber pressure Pd: discharge pressure Fs: solenoid thrust.

[0037]

F0 + (Ps-P0) (S2-S1-S4) +
Pd (S3-S2) + Pc (S4-S3) = Fs According to Equation 6, each port pressure, the urging force of the valve component receiving those pressures, and the solenoid thrust Fs
Are balanced, but the variable width of the suction pressure Ps is substantially determined by the urging force of the bellows assembly 651 and the thrust of the solenoid 653.

The control pressure characteristic shown in FIG.
In controlling s, the discharge pressure Pd and the crankcase pressure Pc
This is an example in which the influence of is eliminated. Each pressure receiving area S at this time
2, S3, S4, S2 = S3 = S4, Equation 6
Is given by Equation 7.

[0039]

F0−S1 · (Ps−P0) = Fs Here, assuming that the suction pressure Ps is Ps1, Equation 7 becomes Equation 8.

[0040]

F0−S1 · (Ps1−P0) = Fs1 Here, assuming that the suction pressure Ps is Ps2, Equation 7
Is given by Expression 9.

[0041]

F0−S1 · (Ps2−P0) = Fs2 Therefore, the variable width Ps1−Ps2 of the suction pressure Ps is as shown in Expression 10.

[0042]

Ps1−Ps2 = (Fs2−Fs1) / S1 From Expression 10, the variable width of the suction pressure Ps is expressed by the thrust variable width (Fs2−Fs1) of the solenoid and the bellows pressure receiving area S.
1 will be determined.

Under such a balance system, in the case of the conventional CFC-based refrigerant (R134a), the variable width of the suction pressure Ps needs to be about 5 kgf / cm ² , and the bellows pressure receiving area S1 is about 0.5 cm ² . Therefore, the required thrust difference of the solenoid is about 2.5kgf.

However, when a refrigerant having a high condensing pressure such as carbon dioxide or hydrocarbon is used as the refrigerant, the variable width of the suction pressure Ps needs to be about 20 kgf / cm ² .

At this time, the variable width of the suction pressure Ps is set to 20 kgf / c with the current thrust difference of the solenoid (2.5 kgf).
If the m ^2, the bellows pressure receiving area S1 is 0.125c
m ² , which requires extremely miniaturization, which makes fabrication extremely difficult.

Conversely, if the bellows pressure receiving area S1 is 0.5 cm ² at the present time, the difference in thrust of the solenoid is 10 kg.
f It becomes necessary, which leads to an increase in the size of the solenoid and an increase in required power.

[0047]

Therefore, in the solenoid control valves of the prior arts 1 and 2, when a refrigerant having a high condensing pressure such as carbon dioxide or hydrocarbon is used as the refrigerant, the suction pressure Ps and the crank chamber pressure are reduced. The variable width of the pressure of the control fluid, such as Pc, which becomes the pressure response target becomes large, and it is necessary to reduce the pressure receiving area of the bellows assembly.

However, since it is difficult to make the bellows effective pressure receiving area smaller than a predetermined value, the output characteristics of the bellows (the magnitude of the urging force with respect to the pressure difference) can be freely set, or the solenoid control valve or the solenoid can be used. It has been difficult to increase the durability of the control valve and achieve downsizing.

The present invention has been made in order to solve the above-mentioned problems of the prior art. It is an object of the present invention to expand the pressure range of a control fluid to be pressure-responsive, and to have a small size and durability. It is to provide a solenoid control valve.

[0050]

In order to achieve the above object, according to the present invention, there are provided a plurality of pressure response units each having a movable portion having a different effective pressure receiving area and being displaced in accordance with a pressure difference between two pressure regions. Means and the movable parts of the plurality of pressure response means are connected to each other, and a part of the urging force obtained by each movable part is offset, so that the urging force corresponding to the effective pressure receiving area smaller than the plurality of pressure response means is obtained. Connecting means for obtaining the opening and closing means, valve means for controlling opening and closing in accordance with the urging force of the connecting means, and applying an urging force which varies in accordance with the applied current value to the opening and closing control of the valve means, A solenoid for adjusting the opening and closing control of the control valve.

According to this, it is possible to perform opening / closing control of the valve means in accordance with the pressure of the control fluid to be pressure-responsive and with an urging force corresponding to an effective pressure receiving area smaller than each of the plurality of pressure response means. Become.

Further, the opening / closing control of the valve means can be adjusted by the urging force of the solenoid. That is,
Changing the pressure range of the fluid to be controlled by holding the valve at a position where the urging force by the pressure responsive means and the urging force by the solenoid are balanced, or by changing the urging force required to control the opening and closing of the valve by the pressure responsive object It is possible to expand.

When the urging force of the pressure responsive means and the urging force of the solenoid are balanced, the urging force of the pressure responsive means becomes an urging force corresponding to a small effective pressure receiving area. Can be suppressed, and it is not necessary to increase the urging force of the solenoid, and the size of the solenoid can be reduced.

Therefore, the pressure range of the control fluid to be pressure-responsive can be expanded without increasing the urging force of the solenoid and the like, such as reinforcing the solenoid control valve and holding the position of the valve body. The valve can be made smaller and durable.

[0055] It is also preferable that the plurality of pressure response means are two pressure response means arranged to face each other via a closed pressure region.

Thus, the configuration of the plurality of pressure response means can be made compact.

[0057]

DESCRIPTION OF THE PREFERRED EMBODIMENTS (Embodiment 1) FIG. 1 is an explanatory view of a sectional structure of a solenoid control valve 51, and FIG. The force (hereinafter referred to as fx or Fx) and the effective pressure receiving area (hereinafter referred to as the pressure receiving pressure) of the control fluid in each component member.
It is a schematic diagram explaining the state of Sx) and pressure (hereinafter, described as Px).

The solenoid control valve 51, like the solenoid control valve 600 described in the related art, applies a refrigerant introduced into a variable displacement type compressor used in an air conditioner or the like (cooling device) to a pressure response target. Is performed in response to the suction pressure Ps to the compressor.

In the compressor, the angle of the swash plate changes according to the crank chamber pressure Pc of the crank chamber in which the swash plate is disposed, and the discharge pressure Pd of the refrigerant output from the compressor, that is, the cooling capacity is adjusted. Is what it is.

The solenoid control valve 51 controls opening and closing of a valve section 54 by a bellows assembly 52 responsive to crankcase pressure Pc and a solenoid 53.

The bellows assembly 52 includes, as main components, bellows 52a and 52b as a pair of pressure response means having different effective pressure receiving areas, and a spring 52c for urging the valve body 54a in the valve closing direction. .

The bellows assembly 52 is disposed in the bellows chamber 55, and has two different bellows 52 having different effective pressure receiving areas.
a and 52b are arranged coaxially opposite each other via an annular sleeve 52e. The annular sleeve 52e is fixed inside the bellows chamber 55 via a sleeve 56 whose position can be adjusted in the axial direction.

One end of the bellows 52a, 52b is a fixed end, and is tightly fitted and fixed to the annular sleeve 52e. Further, the other end becomes a movable end as a movable part, is connected by a rod 52d, and is displaced in accordance with a pressure difference between an external atmospheric pressure and an internal pressure of the bellows 52a, 52b as two pressure regions.

The rod 52d is connected to the valve element 54a and urges the valve element 54a in the valve closing direction.

The bellows portions having a proportional relationship with the effective pressure receiving areas of the bellows 52a and 52b have diameters of D bellows, respectively.
1, D2, and in this embodiment, the relationship is D1 <D2. A region surrounded by the bellows 52a, 52b is defined as a sealed pressure region 57 having an internal pressure P0.
And

The pressure in the closed pressure area 57, which is the internal pressure P0, is set to an appropriate value in accordance with the conditions of use of the bellows assembly 52 and the like. Is set as a negative pressure (vacuum) to generate a pressure difference.

The solenoid 53 generates an urging force on the plunger 53b according to the voltage / current applied to the coil 53a. The biasing force of the plunger 53b is transmitted to the valve body 54a in the valve opening direction via the rod 53c.

The balance equation of the pressure control by the solenoid control valve 51 is shown in the following equation (11).

Where, f0: the urging force of the bellows inner spring 52c S1: the pressure receiving area of the bellows 52b S2: the pressure receiving area of the valve 54 S3: the pressure receiving area of the bellows 52a P0: the bellows internal pressure Ps: the suction pressure Pc: the crank chamber pressure Fs: Solenoid thrust.

[0070]

F0- (S1-S3) (Pc-P0) + S2
(Pc−Ps) = Fs In this equation 11, if the difference between the bellows pressure receiving area and the valve section pressure receiving area S2 is defined as S1−S3 = S2,
Equation 11 becomes Equation 12.

[0071]

F0− (S1−S3) (Ps−P0) = Fs Therefore, in order to obtain a control pressure characteristic similar to that in FIG.
Here, assuming that the suction pressure Ps is Ps1, Expression 12 is
Equation 13 is obtained.

[0072]

F0− (S1−S3) (Ps1−P0) = Fs1 Here, assuming that the suction pressure Ps is Ps2, Expression 12 is given by:
Equation 14 is obtained.

[0073]

F0− (S1−S3) (Ps2−P0) = Fs2 Therefore, the variable width Ps1−Ps2 of the suction pressure Ps is represented by Expression 15.

[0074]

Ps1−Ps2 = (Fs2−Fs1) / (S1−S3) From Equation 15, the variable width of the suction pressure Ps is determined by the difference between the thrust variable width (Fs2−Fs1) of the solenoid and the effective pressure receiving area of the bellows. It is determined.

As a result, even if the difference in thrust of the solenoid is small, the difference in the area of the bellows can be reduced to cope with a large variable width of the suction pressure Ps. As a result, the variable width of the suction pressure Ps is increased. It becomes possible. In addition, the size of the solenoid can be easily reduced, the size of the solenoid control valve can be reduced, and the durability can be improved because a large urging force is not applied to the valve portion.

(Embodiment 2) FIG. 3 is an explanatory sectional view of a solenoid control valve 61 according to a second embodiment of the present invention.

The solenoid control valve 61 is provided with a diaphragm assembly 62 similar to that of the second embodiment instead of the bellows assembly, and other configurations, operations and effects are the same as those of the first embodiment. The same is true.

(Embodiment 3) FIG. 4 is an explanatory sectional view of a solenoid control valve 71 according to a third embodiment of the present invention, and FIG. 5 is a schematic view thereof.

The solenoid control valve 71 operates at the suction pressure P
The opening and closing of the valve unit 74 is controlled by the bellows assembly 72 and the solenoid 73 that respond to s.

That is, the biasing force of the bellows assembly 72 is used as the biasing force in the direction to open the valve portion 74, and the thrust of the solenoid 73 disposed opposite to the bellows assembly 72 closes the valve portion 74. Direction biasing force.

The opening / closing force of the valve portion 74 is adjusted by balancing the urging force of the bellows assembly 72 and the thrust of the solenoid 73.

The bellows assembly 72 has bellows 72a, 72b having different effective pressure receiving areas and a spring 72c for urging the bellows 72a in the extending direction as main components.

A bellows output rod 75 is connected to the bellows assembly 72. Between the bellows output rod 75 and the plunger 73a of the solenoid 73, a balance rod 76 having a valve portion 76a (in this embodiment, a bellows output rod 75). The rod 75 and the balance rod 76 are integrally formed).

The bellows chamber 77 and the plunger chamber 73b accommodating the plunger 73a of the solenoid 73 are connected by a passage 78a passing through the valve body 78 in the axial direction and an axial hole 73a1 of the plunger 73a, and are connected to the plunger chamber 73b. Is the suction pressure Ps.

When this solenoid control valve 71 is used for controlling the compressor, the solenoid control valve 71 changes the discharge pressure Pd to the crank chamber pressure P in accordance with the suction pressure Ps.
c to control the pressure in the crank chamber Pc.
To adjust the cooling capacity (pressure adjustment of the discharge pressure Pd) by changing the angle of the swash plate of the compressor. As a result, the suction pressure P
control s.

The balance equation for the pressure control by the solenoid control valve 71 is shown in the following equation (16).

Where f0: bellows inner spring biasing force S1: pressure receiving area of bellows 72a S2: pressure receiving area of bellows output rod 75 S3: pressure receiving area of seal portion of valve 74 S4: pressure receiving area of balance rod 76 S5: bellows 72b Pressure receiving area P0: bellows internal pressure Ps: suction pressure Pc: crank chamber pressure Pd: discharge pressure Fs: solenoid thrust.

[0088]

F0 + (Ps-P0) (S2-S1-S4 +
S5) + Pd (S3-S2) + Pc (S4-S3) = F
s If the pressure receiving areas S2, S3, and S4 are S2 = S3 = S4 in order to obtain the control pressure characteristics shown in FIG. 21, Expression 16 becomes Expression 17.

[0089]

F0 + (Ps−P0) (S5−S1) = Fs Here, assuming that the suction pressure Ps is Ps1, Equation 17 is given by
Equation 18 is obtained.

[0090]

F0 + (Ps1−P0) (S5−S1) = Fs1 Further, if the suction pressure Ps is Ps2, Equation 17
Is given by Expression 19.

[0091]

F0 + (Ps2−P0) (S5−S1) = Fs2 Therefore, the variable width Ps1−Ps2 of the suction pressure Ps is represented by Expression 20.

[0092]

Ps1−Ps2 = (Fs2−Fs1) / (S1−S5) From Expression 20, the variable width of the suction pressure Ps is determined by the difference between the thrust variable width of the solenoid (Fs2−Fs1) and the effective pressure receiving area of the bellows ( S1-S5).

As a result, even if the difference in thrust of the solenoid is small, the difference in the area of the bellows can be reduced to cope with a large variable width of the suction pressure Ps. As a result, the variable width of the suction pressure Ps is increased. It becomes possible.

Further, the size of the solenoid can be easily reduced.
Since no large urging force is applied to the valve portion, durability can be improved.

(Embodiment 4) FIG. 6 is an explanatory sectional view of a solenoid control valve 81 according to a fourth embodiment of the present invention.

The solenoid control valve 81 is provided with a diaphragm assembly 82 similar to that of the second embodiment instead of the bellows assembly 72, and the other structures, operations and effects are the same as those of the third embodiment. Is the same as

(Embodiment 5) FIG. 7 is an explanatory sectional view of a solenoid control valve 91 to which the present invention is applied in a fifth embodiment.

The solenoid control valve 91 is the same as that of the third embodiment except that the positions of the bellows assembly and the valve portion are changed. A bellows assembly 92 is disposed between the solenoid 93 and the valve portion 94. The configuration is as follows.

The other structures, operations and effects are the same as those of the third embodiment.

(Embodiment 6) FIG. 8 is an explanatory sectional view of a solenoid control valve 101 according to a sixth embodiment of the present invention, and FIG. 9 is a schematic view thereof.

The solenoid control valve 101 controls the opening and closing of a valve portion 105 by means of two divided bellows assemblies 102 and 103 responsive to the suction pressure Ps and a solenoid 104.

The structure of the solenoid control valve 101 except for the bellows assembly 103 is the same as the structure of the solenoid control valve 650 of FIG.

And, as a feature of this embodiment,
The bellows assembly 103 disposed in the plunger chamber 104b of the solenoid 104 responds to the same suction pressure Ps as the bellows assembly 102, and applies a biasing force in the opposite direction to the bellows assembly 102 to control the opening and closing of the valve portion 105. .

Each bellows assembly has a bellows 102a,
103a, springs 102b, 103b and terminal member 102
c, 102d, 103c, and 103d.

The bellows assembly 102 and the bellows assembly 103 have different effective pressure receiving areas, and are connected in the axial direction by a plunger 104a, a balance rod 106, and a valve rod 107 which function as connecting means for the two. The biasing force obtained by the bellows assemblies 102 and 103 corresponds to the difference between their effective pressure receiving areas.

The balance equation for pressure control by the solenoid control valve 101 is shown in the following equation (21).

Here, f0: spring biasing force in the bellows 102a f1: spring biasing force in the bellows 103a S1: pressure receiving area of the bellows 102a S2: pressure receiving area of the valve rod 107 S3: seal pressure receiving area of the valve portion 105 S4: Pressure receiving area of balance rod 106 S5: Pressure receiving area of bellows 103a P0: Bellows internal pressure Ps: Suction pressure Pc: Crank chamber pressure Pd: Discharge pressure Fs: Solenoid thrust

[0108]

F0-f1 + (Ps-P0) (S2-S1-
S4 + S5) + Pd (S3-S2) + Pc (S4-S
3) = Fs In order to obtain the control pressure characteristics shown in FIG.
2, S3, S4, S2 = S3 = S4, Equation 2
1 is represented by Expression 22.

[0109]

F0−f1 + (Ps−P0) (S5−S1) = Fs Here, assuming that the suction pressure Ps is Ps1, Expression 22 is given by:
Equation 23 is obtained.

[0110]

F0−f1 + (Ps1−P0) (S5−S1) = Fs1 Further, if the suction pressure Ps is Ps2, the following equation is obtained.
Is given by Equation 24.

[0111]

F0−f1 + (Ps2−P0) (S5−S1) = Fs2 Therefore, the variable width Ps1−Ps2 of the suction pressure Ps is represented by Expression 25.

[0112]

From equation 25, Ps1-Ps2 = (Fs2-Fs1) / (S1-S5) From Equation 25, the variable width of the suction pressure Ps is the difference between the thrust variable width of the solenoid (Fs2-Fs1) and the effective pressure receiving area of the bellows ( S1-S5).

As a result, even if the difference in thrust of the solenoid is small, the area difference between the bellows is reduced, so that it is possible to cope with a large variable width of the suction pressure Ps, and as a result, the variable width of the suction pressure Ps is increased. It becomes possible.

Also, the size of the solenoid can be easily reduced,
Since no large urging force is applied to the valve portion, durability can be improved.

(Embodiment 7) FIG. 10 shows a solenoid control valve 111 according to a seventh embodiment of the present invention.
FIG. 3 is an explanatory view of a cross-sectional configuration of FIG.

The solenoid control valve 111 has a configuration in which diaphragm assemblies 112 and 113 are provided instead of the bellows assemblies 102 and 103 in the sixth embodiment, and other configurations, operations and effects are the same as those in the sixth embodiment. This is the same as the embodiment.

(Eighth Embodiment) FIG. 11 shows a solenoid control valve 121 according to an eighth embodiment of the present invention.
FIG. 3 is an explanatory view of a cross-sectional configuration of FIG.

The solenoid control valve 121 has a configuration in which two bellows assemblies 122 and 123 are arranged in series and adjacent to each other.

Each bellows assembly has a bellows 122a,
123a, springs 122b, 123b and terminal member 122
c, 122d, 123c, and 123d, and the movement of the outer terminal members 122c and 123c is restricted.

Then, the inner terminal members 122d and 123
d is a yoke 12 connected by a connecting rod 124 as connecting means and moving in the axial direction with respect to the valve body.
The urging force of the bellows assemblies 122 and 123 is transmitted to the bellows output rod 127 via the bellows 5 and 126.

Therefore, the solenoid control valve 121 is
With two bellows assemblies 122 and 123 provided in series responsive to the suction pressure Ps and a solenoid 128,
Opening / closing control of the valve unit 129 is performed.

The other structures, operations and effects are the same as those of the sixth embodiment. As in this embodiment, the arrangement position of the bellows assembly can be divided, or the bellows assembly can be adjacently arranged in series, or an arbitrary arrangement can be adopted.

(Embodiment 9) FIG. 12 is an explanatory sectional view of a solenoid control valve 131 according to a ninth embodiment. The present invention is applied to a solenoid control valve 600 shown in FIG. Things. FIG. 13 is a schematic diagram of the solenoid control valve 131.

The solenoid control valve 131 is made up of two divided bellows assemblies 132 and 133 responsive to the crankcase pressure Pc and a solenoid 134.
Open / close control of the valve unit 135 is performed.

As a feature of this embodiment, the bellows assembly 133 disposed in the plunger chamber 134b of the solenoid 134 responds to the same crank chamber pressure Pc as the bellows assembly 132, and in the opposite direction to the bellows assembly 132. Is applied to the opening / closing control of the valve section 135.

Each bellows assembly has a bellows 132a,
133a, springs 132b, 133b and end member 132
c, 132d, 133c, and 133d.

The bellows assembly 132 and the bellows assembly 133 have different effective pressure receiving areas, and are connected in the axial direction by a plunger 134a and a balance rod 136 functioning as connecting means for the two, and the two bellows assemblies 132 , 133 correspond to the difference between their effective pressure receiving areas.

The balance equation for pressure control by the solenoid control valve 131 is shown in the following equation (26).

Where f0: biasing force of the inner spring of the bellows 132a f1: biasing force of the inner spring of the bellows 133a S1: pressure receiving area of the bellows 122a S2: pressure receiving area of the seal portion of the valve portion 105 S3: pressure receiving area of the balance rod 136 S4: bellows 133a Pressure receiving area P0: bellows internal pressure Ps: suction pressure Pc: crank chamber pressure Fs: solenoid thrust.

[0130]

F0-f1- (Pc-P0) (S1-S4)
+ (Pc−Ps) (S2−S3) = Fs In order to obtain the control pressure characteristics shown in FIG.
If S1, S2, S3, and S4 are S1-S4 = S2-S3, Equation 26 becomes Equation 27.

[0131]

F0−f1− (Ps−P0) (S1−S4) = Fs Here, assuming that the suction pressure Ps is Ps1, Equation 27 is given by:
Equation 28 is obtained.

[0132]

F0−f1 + (Ps1−P0) (S1−S4) = Fs1 Further, if the suction pressure Ps is Ps2, Equation 27 is obtained.
Is given by Expression 29.

[0133]

F0−f1 + (Ps2−P0) (S1−S4) = Fs2 Therefore, the variable width Ps1−Ps2 of the suction pressure Ps is as shown in Expression 30.

[0134]

Ps1−Ps2 = (Fs2−Fs1) / (S1−S4) According to Equation 30, the variable width of the suction pressure Ps is the difference between the thrust variable width of the solenoid (Fs2−Fs1) and the effective pressure receiving area of the bellows ( S1-S4).

As a result, even if the difference in thrust of the solenoid is small, the difference in the area of the bellows can be reduced to cope with a large variable width of the suction pressure Ps. As a result, the variable width of the suction pressure Ps is increased. It becomes possible.

Also, the size of the solenoid can be easily reduced,
Since no large urging force is applied to the valve portion, durability can be improved.

(Embodiment 10) FIG. 14 shows a solenoid control valve 1 according to a tenth embodiment of the present invention.
FIG. 41 is an explanatory view of a cross-sectional configuration of 41.

The solenoid control valve 141 has a configuration in which diaphragm assemblies 142 and 143 are provided instead of the bellows assemblies 132 and 133 in the ninth embodiment, and the other configurations, operations, and effects are the same as those in the ninth embodiment. This is the same as the embodiment.

(Embodiment 11) FIG. 15 shows a solenoid control valve 1 according to an eleventh embodiment to which the present invention is applied.
It is sectional drawing explanatory drawing of 51.

The solenoid control valve 151 is the same as the ninth embodiment except that the solenoid control valve 151 is provided with bellows assemblies 152 and 153 arranged in series, similar to the eighth embodiment. Are the same as in the ninth embodiment.

[0141]

According to the present invention described above, the pressure range of the control fluid to be pressure-responsive is expanded,
In addition, it is possible to provide a small and durable solenoid control valve.

The opening / closing control of the valve means can be adjusted by the urging force of the solenoid. In other words, the valve body is held at a position where the urging force of the pressure responsive means and the urging force of the solenoid are balanced, or the urging force required to control the opening and closing of the valve body by the pressure responsive object is changed to change the pressure range of the fluid to be controlled. It can be changed or expanded.

In the case where the urging force of the pressure responsive means and the urging force of the solenoid are balanced, the urging force of the pressure responsive means becomes an urging force corresponding to a small effective pressure receiving area. Can be suppressed, and it is not necessary to increase the urging force of the solenoid, and the size of the solenoid can be reduced.

Therefore, the pressure range of the control fluid to be pressure-responsive can be expanded without increasing the urging force of the solenoid and the like, such as reinforcing the solenoid control valve and holding the position of the valve body. It is possible to reduce the size and durability of the valve.

With the two pressure response means arranged opposite to each other via the closed pressure region, the structure of the plurality of pressure response means can be made compact.

[Brief description of the drawings]

FIG. 1 is a cross-sectional configuration explanatory view of a solenoid control valve according to a first embodiment.

FIG. 2 is a schematic diagram illustrating a state of a biasing force of a solenoid control valve according to the first embodiment.

FIG. 3 is an explanatory sectional view of a solenoid control valve according to a second embodiment.

FIG. 4 is an explanatory cross-sectional configuration diagram of a solenoid control valve according to a third embodiment.

FIG. 5 is a schematic diagram illustrating a state of a biasing force of a solenoid control valve according to a third embodiment.

FIG. 6 is a sectional configuration explanatory view of a solenoid control valve according to a fourth embodiment.

FIG. 7 is an explanatory cross-sectional configuration diagram of a solenoid control valve according to a fifth embodiment.

FIG. 8 is a sectional configuration explanatory view of a solenoid control valve according to a sixth embodiment.

FIG. 9 is a schematic diagram illustrating a state of a biasing force of a solenoid control valve according to a sixth embodiment.

FIG. 10 is a cross-sectional configuration explanatory view of a solenoid control valve according to a seventh embodiment.

FIG. 11 is a sectional configuration explanatory view of a solenoid control valve according to an eighth embodiment.

FIG. 12 is an explanatory sectional view showing a configuration of a solenoid control valve according to a ninth embodiment;

FIG. 13 is a schematic diagram illustrating the state of the urging force of a solenoid control valve according to a ninth embodiment.

FIG. 14 is an explanatory cross-sectional configuration diagram of a solenoid control valve according to a tenth embodiment.

FIG. 15 is an explanatory cross-sectional configuration diagram of a solenoid control valve according to an eleventh embodiment.

FIG. 16 is an explanatory cross-sectional configuration diagram of a solenoid control valve according to Prior Art 1.

FIG. 17 is a schematic diagram illustrating a state of the urging force of a solenoid control valve according to the related art 1.

FIG. 18 is a diagram showing a control pressure characteristic.

FIG. 19 is a cross-sectional configuration explanatory view of a solenoid control valve according to Conventional Technique 2.

FIG. 20 is a schematic diagram illustrating the state of the urging force of a solenoid control valve according to the conventional technique 2.

FIG. 21 is a diagram showing control pressure characteristics.

[Explanation of symbols]

 51 solenoid control valve 52 bellows assembly 52a, 52b bellows 52c spring 52d rod 52e annular sleeve 53 solenoid 54 valve portion 54a valve body 55 bellows chamber 56 sleeve 61 solenoid control valve 62 diaphragm assembly 71 solenoid control valve 72 bellows assembly 72a, 72b bellows 73 solenoid 73a plunger 74 valve part 75 bellows output rod 76 balance rod 76a valve body part 77 bellows chamber 78 valve body 81 solenoid control valve 82 diaphragm assembly 91 solenoid control valve 92 bellows assembly 93 solenoid 94 valve part 101 solenoid control Valves 102, 103 Bellows assembly 102a, 103a Bellows 102b, 103b Spring 102c, 102d, 103c 103d Terminal member 104 Solenoid 104a Plunger 105 Valve section 106 Balance rod 107 Valve rod 111 Solenoid control valve 112,113 Diaphragm assembly 121 Solenoid control valve 122,123 Bellows assembly 122a, 123a Bellows 122b, 123b Spring 122c, 122d, 123c, 123d Terminal member 125, 126 Yoke 127 Bellows output rod 128 Solenoid 129 Valve section 131 Solenoid control valve 132, 133 Bellows assembly 132a, 133a Bellows 132b, 133b Spring 132c, 132d, 133c, 133d Terminal member 134 Solenoid 135 Valve section 136 Balance Rod 141 Solenoid control valve 142, 143 Diaphragm assembly 151 Solenoids control valve 152, 153 bellows assembly

Claims (2)

[Claims] 1. A plurality of pressure responsive means having different effective pressure receiving areas and having movable parts displaced in accordance with a pressure difference between two pressure regions, and a movable part of the plurality of pressure responsive means are connected to each other. Connecting means for canceling a part of the urging force obtained by the movable portion to obtain an urging force corresponding to an effective pressure receiving area smaller than the plurality of pressure response means, and opening and closing in accordance with the urging force of the connection means A valve means to be controlled, and a solenoid for adjusting the opening / closing control of the solenoid control valve by applying an urging force that changes according to the applied current value to the opening / closing control of the valve means. Solenoid control valve. 2. The solenoid control valve according to claim 1, wherein the plurality of pressure responsive means are two pressure responsive means arranged to face each other via a closed pressure region.